EP0639115B1 - Apparatus for refining fiber material - Google Patents
Apparatus for refining fiber material Download PDFInfo
- Publication number
- EP0639115B1 EP0639115B1 EP93910500A EP93910500A EP0639115B1 EP 0639115 B1 EP0639115 B1 EP 0639115B1 EP 93910500 A EP93910500 A EP 93910500A EP 93910500 A EP93910500 A EP 93910500A EP 0639115 B1 EP0639115 B1 EP 0639115B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- bearing
- refining
- bearings
- prestressing
- bearing seat
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
Links
- 238000007670 refining Methods 0.000 title claims abstract description 38
- 239000002657 fibrous material Substances 0.000 title claims abstract description 4
- 238000004519 manufacturing process Methods 0.000 description 2
- 230000006870 function Effects 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 230000013707 sensory perception of sound Effects 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C25/00—Bearings for exclusively rotary movement adjustable for wear or play
- F16C25/06—Ball or roller bearings
- F16C25/08—Ball or roller bearings self-adjusting
-
- D—TEXTILES; PAPER
- D21—PAPER-MAKING; PRODUCTION OF CELLULOSE
- D21D—TREATMENT OF THE MATERIALS BEFORE PASSING TO THE PAPER-MAKING MACHINE
- D21D1/00—Methods of beating or refining; Beaters of the Hollander type
- D21D1/20—Methods of refining
- D21D1/30—Disc mills
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
- F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
- F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
- F16C35/07—Fixing them on the shaft or housing with interposition of an element
- F16C35/077—Fixing them on the shaft or housing with interposition of an element between housing and outer race ring
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
- F16C19/30—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for axial load mainly
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
- F16C23/06—Ball or roller bearings
- F16C23/08—Ball or roller bearings self-adjusting
- F16C23/082—Ball or roller bearings self-adjusting by means of at least one substantially spherical surface
- F16C23/086—Ball or roller bearings self-adjusting by means of at least one substantially spherical surface forming a track for rolling elements
Definitions
- This invention relates to an apparatus for the refining of fiber material.
- the apparatus a so-called disk refiner, comprises two opposed refining disks, at least one of which is rotary and supported on a rotary shaft.
- the shaft is mounted in a stand via a bearing housing comprising at least two bearings, one of which is an axial/radial bearing for carrying axial forces from the refiner disk as well as prevailing radial forces, and one is an axial/radial bearing intended primarily to carry radial forces.
- a disk refiner equipped with such a bearing type is disclosed in SE-PS 345 892.
- the bearing is relatively complicated, because it comprises a bearing housing for the bearings which is axially movable in the refiner stand.
- the bearing housing there must be extensive in length and include several slide surfaces to be fitted into the stand.
- the bearings furthermore, must be axially prestressed in such a way, that at least one bearing must carry radial load and simultaneously must be axially movable in the bearing housing. This compromise renders a complicated and more expensive structure and deteriorates its functional efficiency.
- the present invention offers a solution of the aforesaid problems. Due to the bearing housing being fixed in the stand, and the bearings rigidly mounted each in its axially movable bearing seat, and prestressing members arranged between the bearing seats, a simple and operationally reliable structure is obtained.
- the characterizing features of the invention are apparent from the attached claims.
- Both embodiments consist of a refiner with a stand 1 and a refiner housing 2, in which two opposed refining disks 3,4 are located.
- a first refining disk 3 is rotary
- a second one 4 is stationary.
- the rotary refining disk 3 is supported on a rotary shaft 5, which is mounted in the stand 1 via a bearing housing 6 and driven by a motor (not shown).
- the refining disks 3,4 are provided on their surfaces facing toward each other with refining elements 7,8, which between themselves define a refining gap.
- the stationary refining disk 4 has a central inlet opening 9, through which the material is fed in which is to be refined during its passage outward through the refining gap.
- the rotary shaft 5 also is movable so as to allow adjustment of the refining gap between the refining elements 7,8 on the refining disks 3,4.
- the shaft 5 is supported by two bearings 11,12.
- the first bearing 11 is an axial/radial bearing intended to carry axial forces from the first refining disk 3. This bearing 11 also shall carry prevailing radial forces, for example the dead weight of the shaft and refining disk.
- the second bearing 12 is an axial/radial bearing intended primarily to carry radial forces, for example counter forces to the radial forces on the first bearing.
- the bearing housing 6 is mounted rigidly in the stand 1.
- the two bearings 11,12 are attached with their inner ring on the shaft 5 and with their outer ring are fixed in a first and, respectively, second bearing seat 21,22.
- These bearing seats are axially movable by means of slip fit, but not rotary in the bearing housing 6.
- a plurality of first prestressing members 25 are arranged between the two bearing seats 21,22.
- Each prestressing member 25 preferably is designed as a spring-loaded piston/cylinder unit, the object of which is to keep apart the bearing seats 21,22 so as to prevent play.
- the axial movement of the bearing seats 21,22 is controlled by a first and, respectively, second ring piston 41,42, which are rigidly connected to the bearing housing 6 and thereby cooperate with a first and, respectively, second annular hydraulic cylinder 31,32 in the first and, respectively, second bearing seat 21,22.
- the first ring piston/ring cylinder unit 41,31 is intended to move the first bearing seat 21 so as to reduce the refining gap. This implies, that the axial forces generated in the refining gap are to be taken up via the first ring piston/ring cylinder unit 41,31.
- the second ring piston/ring cylinder unit 42,32 is intended to act in the opposite direction and, thus, is utilized when the refining disks are to be pulled apart.
- a first and, respectively, second conduit 51,52 for hydraulic medium are arranged for operating the two ring piston/ring cylinder units 41,42, 31,32.
- Said conduits extend through the stand 1 via the bearing housing 6 and respective ring piston 41,42 to respective ring cylinder 31,32.
- the two bearing seats 21,22 with associated bearings 11,12 can rapidly and safely be operated as one unit by means of the hydraulic medium in the two conduits 51,52. Simultaneously, the axial forces from the first refining disk 3 are transferred through the bearing 11 and bearing seat 21 to the stationary bearing housing 6.
- the embodiment according to Fig. 2 agrees in principle with Fig. 1.
- a distinguishing feature is that the shaft 5 is supported on three bearings 11,12,13.
- the first bearing 11 is an axial/radial bearing intended to carry part of the axial forces from the first refining disk 3. As in the case of the first embodiment, the bearing 11 shall carry also prevailing radial forces.
- the second bearing 12 is an axial/radial bearing intended primarily to carry radial forces.
- the third bearing 13 is located between the two firstmentioned hearings and arranged to carry only axial forces.
- the third bearing 13 is attached with its inner ring on the shaft 5 and with its outer ring secured in a third bearing seat 23.
- This third bearing seat 23 is axially movable with a certain play in the bearing housing 6.
- a plurality of second and, respectively, third prestressing members 26,27 are located between the first and third bearing seat 21,23 and, respectively, between the second and third bearing seat 22,23.
- the prestressing members preferably are designed as spring-loaded piston/cylinder units and capable to keep the bearing seats 21,22,23 apart from each in order to avoid play.
- the collective force from the third prestressing members 27 shall exceed the collective force from the second prestressing members 26.
- the third bearing seat 23 is formed with a third annular hydraulic cylinder 33, which co-operates with a third ring piston 43 rigidly connected with the bearing housing 6.
- the third ring piston/ring cylinder 43,33 is moved by means of a hydraulic medium via a third supply conduit 53.
- the third ring piston/ring cylinder unit 43,33 further is arranged to co-operate with the first ring piston/ring cylinder unit 41,31 in order to take up axial forces from the first refining disk 3.
- the distribution of the axial forces from the first and third bearing 11,13 is determined by the ratio between the areas in the first and third ring cylinder 31,33 by maintaining the same pressure in the respective conduit 51,53.
- the load distribution then is directly proportional to the area ratio.
- the third bearing 13 does not carry any radial forces, because the bearing seat 23 is located with play in the bearing housing 6.
- it may be suitable to design the third ring cylinder 33 with a slightly greater area than the first ring cylinder 31, so that the axial load on the third bearing is slightly greater.
- the bearing detail according to Fig. 2 shown in Fig. 3 comprises the two bearing seats 22,23 and one prestressing member 27.
- the prestressing members 27 are formed with a piston/piston rod 61, the rear end 62 of which abuts the bearing seat 22, and its forward end is axially movable in a cylinder 63.
- a prestressed spring package 64 is located which tends to press apart the piston/piston rod 61 and cylinder 63, and therewith also the bearing seats 22 and 23, so that play in the bearings 12,13 is avoided.
- the remaining prestressing members 25,26 are designed and operate correspondingly. This operational function is essential when the first refining disk 3 is moved axially towards the second refining disk 4 for adjusting the refining gap before the production is started, because the pressure in the ring cylinders 31,33 then is very low.
- Fig. 4 shows how such a relief can be provided.
- Fig. 4 shows the same detail of the bearing as in Fig. 3, but the prestressing member 27 is designed differently.
- a piston rod 65 abuts the bearing seat 22 with its rear end 66.
- the forward end of the piston rod is formed with a piston 67, which is axially movable in a cylinder 68.
- a prestressed spring package 64 is located between the rear end 66 of the piston rod and the cylinder 68.
- the cylinder 68 communicates via a channel 69 with the space in the ring cylinder 33 in front of the ring piston 43.
- the pressure in the cylinder 68 increases simultaneously and thereby counteracts the force of the spring package 64.
- the remaining prestressing members 25,26 can be designed in a corresponding manner, thereby avoiding unnecessary axial load on the bearings during operation.
- the collective force from the prestressing members 27 all the time shall exceed the collective force from the prestressing members 26.
Landscapes
- General Engineering & Computer Science (AREA)
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Support Of The Bearing (AREA)
- Paper (AREA)
- Artificial Filaments (AREA)
- Preliminary Treatment Of Fibers (AREA)
- Polishing Bodies And Polishing Tools (AREA)
- Yarns And Mechanical Finishing Of Yarns Or Ropes (AREA)
- Spinning Methods And Devices For Manufacturing Artificial Fibers (AREA)
- Constituent Portions Of Griding Lathes, Driving, Sensing And Control (AREA)
- Rolling Contact Bearings (AREA)
- Grinding Of Cylindrical And Plane Surfaces (AREA)
Abstract
Description
- This invention relates to an apparatus for the refining of fiber material. The apparatus, a so-called disk refiner, comprises two opposed refining disks, at least one of which is rotary and supported on a rotary shaft. In a disk refiner of said type, the shaft is mounted in a stand via a bearing housing comprising at least two bearings, one of which is an axial/radial bearing for carrying axial forces from the refiner disk as well as prevailing radial forces, and one is an axial/radial bearing intended primarily to carry radial forces.
- A disk refiner equipped with such a bearing type is disclosed in SE-PS 345 892. The bearing is relatively complicated, because it comprises a bearing housing for the bearings which is axially movable in the refiner stand. The bearing housing there must be extensive in length and include several slide surfaces to be fitted into the stand. The bearings, furthermore, must be axially prestressed in such a way, that at least one bearing must carry radial load and simultaneously must be axially movable in the bearing housing. This compromise renders a complicated and more expensive structure and deteriorates its functional efficiency.
- An apparatus according to the preamble of claim 1 is disclosed in SE-B-462572.
- The present invention offers a solution of the aforesaid problems. Due to the bearing housing being fixed in the stand, and the bearings rigidly mounted each in its axially movable bearing seat, and prestressing members arranged between the bearing seats, a simple and operationally reliable structure is obtained. The characterizing features of the invention are apparent from the attached claims.
- The invention is described in greater detail in the following, with reference to the accompanying drawings showing different embodiments of the invention.
- Figs. 1 and, respectively, 2 are cross-sections of embodiments comprising two and, respectively, three bearings.
- Figs. 3 and 4 are cross-sections of a detail in Fig. 2 of different designs.
- Both embodiments consist of a refiner with a stand 1 and a refiner housing 2, in which two opposed
refining disks 3,4 are located. At these embodiments, afirst refining disk 3 is rotary, and a second one 4 is stationary. Therotary refining disk 3 is supported on arotary shaft 5, which is mounted in the stand 1 via a bearinghousing 6 and driven by a motor (not shown). - The
refining disks 3,4 are provided on their surfaces facing toward each other with refining elements 7,8, which between themselves define a refining gap. The stationary refining disk 4 has a central inlet opening 9, through which the material is fed in which is to be refined during its passage outward through the refining gap. - During the refining operation, a very high pressure is generated in the refining gap, which pressure yields an axial force which has to be carried by the bearing of the shaft. This force can amount to several tens of tons and, therefore, puts very high requirements on the bearing design.
- The
rotary shaft 5 also is movable so as to allow adjustment of the refining gap between the refining elements 7,8 on therefining disks 3,4. - According to the embodiment shown in Fig. 1, the
shaft 5 is supported by twobearings disk 3. This bearing 11 also shall carry prevailing radial forces, for example the dead weight of the shaft and refining disk. The second bearing 12 is an axial/radial bearing intended primarily to carry radial forces, for example counter forces to the radial forces on the first bearing. - The bearing
housing 6 is mounted rigidly in the stand 1. The twobearings shaft 5 and with their outer ring are fixed in a first and, respectively, second bearingseat housing 6. In the stationary bearinghousing 6, a plurality of firstprestressing members 25 are arranged between the two bearingseats prestressing member 25 preferably is designed as a spring-loaded piston/cylinder unit, the object of which is to keep apart thebearing seats - The axial movement of the
bearing seats second ring piston housing 6 and thereby cooperate with a first and, respectively, second annularhydraulic cylinder seat ring cylinder unit seat 21 so as to reduce the refining gap. This implies, that the axial forces generated in the refining gap are to be taken up via the first ring piston/ring cylinder unit ring cylinder unit - A first and, respectively,
second conduit ring cylinder units housing 6 andrespective ring piston respective ring cylinder - Owing to this design, the two bearing
seats bearings conduits disk 3 are transferred through thebearing 11 and bearingseat 21 to the stationary bearinghousing 6. - The embodiment according to Fig. 2 agrees in principle with Fig. 1. A distinguishing feature is that the
shaft 5 is supported on threebearings disk 3. As in the case of the first embodiment, the bearing 11 shall carry also prevailing radial forces. The second bearing 12 is an axial/radial bearing intended primarily to carry radial forces. The third bearing 13 is located between the two firstmentioned hearings and arranged to carry only axial forces. Thebearing 13, however, preferably is an axial/radial bearing. - The third bearing 13 is attached with its inner ring on the
shaft 5 and with its outer ring secured in a third bearingseat 23. This third bearingseat 23 is axially movable with a certain play in the bearinghousing 6. According to this embodiment, a plurality of second and, respectively, thirdprestressing members 26,27 are located between the first and third bearingseat seat bearing seats prestressing members 27 shall exceed the collective force from the second prestressing members 26. - The third bearing
seat 23 is formed with a third annularhydraulic cylinder 33, which co-operates with athird ring piston 43 rigidly connected with thebearing housing 6. The third ring piston/ring cylinder third supply conduit 53. The third ring piston/ring cylinder unit ring cylinder unit first refining disk 3. - The distribution of the axial forces from the first and third bearing 11,13 is determined by the ratio between the areas in the first and
third ring cylinder respective conduit bearing seat 23 is located with play in the bearinghousing 6. As the first bearing 11 carries also radial forces, it may be suitable to design thethird ring cylinder 33 with a slightly greater area than thefirst ring cylinder 31, so that the axial load on the third bearing is slightly greater. - It is, of course, possible to arrange additional bearings between the first and second bearing 11,12. These additional bearings with associated bearing seats then, like the third bearing, shall carry only axial forces, which are distributed in proportion to the area of the respective ring piston/ring cylinder unit. Prestressing members between the bearing seats are arranged as described above.
- The bearing detail according to Fig. 2 shown in Fig. 3 comprises the two bearing
seats prestressing member 27. According to this embodiment, theprestressing members 27 are formed with a piston/piston rod 61, therear end 62 of which abuts thebearing seat 22, and its forward end is axially movable in acylinder 63. Between therear end 62 of the piston rod and thecylinder 63, aprestressed spring package 64 is located which tends to press apart the piston/piston rod 61 andcylinder 63, and therewith also thebearing seats bearings prestressing members 25,26 are designed and operate correspondingly. This operational function is essential when thefirst refining disk 3 is moved axially towards the second refining disk 4 for adjusting the refining gap before the production is started, because the pressure in thering cylinders - At the start of the production, the pressure in the
ring cylinders prestressing members bearing 12. It is, therefore, possible to arrange a relief of at least some of theprestressing members member 27 is designed differently. A piston rod 65 abuts the bearingseat 22 with its rear end 66. The forward end of the piston rod is formed with a piston 67, which is axially movable in a cylinder 68. Between the rear end 66 of the piston rod and the cylinder 68, aprestressed spring package 64 is located. The cylinder 68 communicates via a channel 69 with the space in thering cylinder 33 in front of thering piston 43. At increasing pressure in thering cylinder 33, the pressure in the cylinder 68 increases simultaneously and thereby counteracts the force of thespring package 64. The remainingprestressing members 25,26, of course, can be designed in a corresponding manner, thereby avoiding unnecessary axial load on the bearings during operation. As regards the embodiment according to Fig. 2, the collective force from theprestressing members 27 all the time shall exceed the collective force from the prestressing members 26.
Claims (7)
- Apparatus for refining fiber material, comprising two opposed refining disks (3,4), at least a first one (3) of which is rotary and supported on a rotary shaft (5), which is mounted in a stand (1) via a bearing housing (6) comprising at least two bearings (11,12,13), a first bearing (11) of which is an axial/radial bearing intended to carry axial forces from the first refining disk (3) as well as prevailing radial forces, and a second bearing (12) is an axial/radial bearing primarily intended to carry radial forces, characterized in that the bearings (11,12,13) are rigidly mounted each in its bearing seat (21,22,23) so that each bearing seat is axially movable in the bearing housing (6), which in its turn is mounted stationary in the stand (1), and that prestressing members (25,26,27) are arranged between the bearing seats (21,22,23).
- Apparatus as defined in claim 1, characterized in that a third bearing (13) for carrying only axial forces from the refining disk (3) is located in a third bearing seat (23) between the first and second bearing (11,12) and, respectively, bearing seat (21,22).
- Apparatus as defined in claim 1 or 2, characterized in that each bearing seat (21,22,23) is capable to be moved axially by means of an annular hydraulic cylinder (31,32,33), which is connected to a conduit (51,52,53) for hydraulic medium and co-operates with a ring piston (41,42,43) rigidly connected to the bearing housing (6).
- Apparatus as defined in claim 3 comprising three bearings (11,12,13) and, respectively, bearing seats (21,22,23), characterized in that the annular hydraulic cylinders (31,33) in the first and, respectively, third bearing seat (21,23) are dimensioned for distributing the axial forces between the first and, respectively, third bearing (11,13).
- Apparatus as defined in claim 2, characterized in that one or more additional bearings for carrying only axial forces from the refining disk (3) are located each in its bearing seat between the first and second bearing (11,12) and, respectively, bearing seat (21,22).
- Apparatus as defined in any one of the preceding claims, characterized in that each prestressing member (25,26,27) is formed with a piston/cylinder unit, and the prestressing is brought about by a spring package (64), which is capable to press apart the piston (61,66) and cylinder (63,68).
- Apparatus as defined in claim 6, characterized in that at least some of the cylinders (68) of the prestressing members (25,26,27) communicate via a channel (69) with the first and, respectively, third ring cylinder (31,33), so that the pressure in said ring cylinders counteracts the prestressing in the prestressing members (25,26,27).
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
SE9201448A SE470054B (en) | 1992-05-08 | 1992-05-08 | Apparatus for refining fiber material comprising two opposing grinding wheels, at least one of which is supported by a rotatable shaft stored in a frame |
SE9201448 | 1992-05-08 | ||
PCT/SE1993/000344 WO1993023166A1 (en) | 1992-05-08 | 1993-04-21 | Apparatus for refining fiber material |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0639115A1 EP0639115A1 (en) | 1995-02-22 |
EP0639115B1 true EP0639115B1 (en) | 1997-03-26 |
Family
ID=20386183
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP93910500A Expired - Lifetime EP0639115B1 (en) | 1992-05-08 | 1993-04-21 | Apparatus for refining fiber material |
Country Status (12)
Country | Link |
---|---|
US (1) | US5472285A (en) |
EP (1) | EP0639115B1 (en) |
JP (1) | JPH07506291A (en) |
AT (1) | ATE150668T1 (en) |
AU (1) | AU4097093A (en) |
CA (1) | CA2133201A1 (en) |
DE (1) | DE69309264T2 (en) |
ES (1) | ES2099437T3 (en) |
FI (1) | FI945225A0 (en) |
NO (1) | NO303678B1 (en) |
SE (1) | SE470054B (en) |
WO (1) | WO1993023166A1 (en) |
Families Citing this family (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP3604431B2 (en) * | 1994-12-13 | 2004-12-22 | 光洋精工株式会社 | Preloading device for rolling bearings |
SE504801C2 (en) * | 1995-08-21 | 1997-04-28 | Sunds Defibrator Ind Ab | Measuring device for refiners |
ES2688229T3 (en) * | 2009-07-31 | 2018-10-31 | Mts Systems Corporation | Test assembly of the drive train of a wind turbine |
SE536186C2 (en) * | 2011-11-30 | 2013-06-18 | Metso Paper Sweden Ab | Stand for a refining apparatus for decomposing and refining lignocellulosic material |
CN104258925B (en) * | 2014-09-30 | 2016-09-28 | 湖南清河重工机械有限公司 | For pulverizing the spinning roller grinding machine of powder body sinter |
CN113164967B (en) * | 2020-04-01 | 2022-02-25 | 安德里茨股份公司 | Device for grinding fibrous material suspensions |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2565759A (en) * | 1949-09-29 | 1951-08-28 | Danly Mach Specialties Inc | Flywheel bearing demounting assembly |
US3304139A (en) * | 1964-06-22 | 1967-02-14 | Torrington Co | Mounting for multiple-row roller bearings |
SE345892B (en) * | 1970-10-26 | 1972-06-12 | Defibrator Ab | |
US4341426A (en) * | 1980-10-22 | 1982-07-27 | The Timken Company | Clamp-up device for roll neck bearings |
SE462572B (en) * | 1988-05-03 | 1990-07-16 | Skf Ab | DEVICE FOR TWO PAIRS INSTALLED ROLLING STORAGE TAKING UP TO AXIAL AND RADIAL LOADING |
SE467343B (en) * | 1990-10-03 | 1992-07-06 | Sunds Defibrator Ind Ab | STORAGE SYSTEM IN A REFINING DEVICE FOR PREPARING PULP |
-
1992
- 1992-05-08 SE SE9201448A patent/SE470054B/en unknown
-
1993
- 1993-04-21 AT AT93910500T patent/ATE150668T1/en not_active IP Right Cessation
- 1993-04-21 DE DE69309264T patent/DE69309264T2/en not_active Expired - Fee Related
- 1993-04-21 EP EP93910500A patent/EP0639115B1/en not_active Expired - Lifetime
- 1993-04-21 AU AU40970/93A patent/AU4097093A/en not_active Abandoned
- 1993-04-21 ES ES93910500T patent/ES2099437T3/en not_active Expired - Lifetime
- 1993-04-21 WO PCT/SE1993/000344 patent/WO1993023166A1/en active IP Right Grant
- 1993-04-21 US US08/331,652 patent/US5472285A/en not_active Expired - Fee Related
- 1993-04-21 CA CA002133201A patent/CA2133201A1/en not_active Abandoned
- 1993-04-21 JP JP5515152A patent/JPH07506291A/en active Pending
-
1994
- 1994-11-07 FI FI945225A patent/FI945225A0/en unknown
- 1994-11-07 NO NO944242A patent/NO303678B1/en unknown
Also Published As
Publication number | Publication date |
---|---|
CA2133201A1 (en) | 1993-11-25 |
DE69309264D1 (en) | 1997-04-30 |
DE69309264T2 (en) | 1997-07-03 |
ATE150668T1 (en) | 1997-04-15 |
JPH07506291A (en) | 1995-07-13 |
FI945225A (en) | 1994-11-07 |
SE9201448L (en) | 1993-11-01 |
FI945225A0 (en) | 1994-11-07 |
SE9201448D0 (en) | 1992-05-08 |
AU4097093A (en) | 1993-12-13 |
SE470054B (en) | 1993-11-01 |
US5472285A (en) | 1995-12-05 |
NO944242L (en) | 1994-11-07 |
EP0639115A1 (en) | 1995-02-22 |
NO303678B1 (en) | 1998-08-17 |
ES2099437T3 (en) | 1997-05-16 |
NO944242D0 (en) | 1994-11-07 |
WO1993023166A1 (en) | 1993-11-25 |
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